CN102996789A - Hydraulic actuation device for actuating clutches, particularly in a multi-clutch transmission system for motor vehicles - Google Patents
Hydraulic actuation device for actuating clutches, particularly in a multi-clutch transmission system for motor vehicles Download PDFInfo
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- CN102996789A CN102996789A CN2012101850470A CN201210185047A CN102996789A CN 102996789 A CN102996789 A CN 102996789A CN 2012101850470 A CN2012101850470 A CN 2012101850470A CN 201210185047 A CN201210185047 A CN 201210185047A CN 102996789 A CN102996789 A CN 102996789A
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- clutch
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- pressure circuit
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D48/00—External control of clutches
- F16D48/02—Control by fluid pressure
- F16D48/0206—Control by fluid pressure in a system with a plurality of fluid-actuated clutches
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D48/00—External control of clutches
- F16D48/02—Control by fluid pressure
- F16D2048/0257—Hydraulic circuit layouts, i.e. details of hydraulic circuit elements or the arrangement thereof
- F16D2048/0269—Single valve for switching between fluid supply to actuation cylinder or draining to the sump
Abstract
The invention discloses a hydraulic actuation device (10) for actuating clutches (12, 12'), particularly in a multi-clutch transmission system for motor vehicles. The device (10) has two pressure circuits (16,16) that are hydraulically connected with pump (14) and a reservoir (18) from which the hydraulic fluid is conveyed by the pump to the pressure circuit. The pressure circuit comprises a non-return valve (20,20) blocking in the direction of the pump, an electromagnetically actuable proportional throttle valve (22,22). The pump drive and proportional throttle valve are electrically connected with a control unit which co-ordinates the electrical activation of the pump drive and the proportional throttle valves. It is thus possible in conceptually simple manner and with comparatively low outlay on technical hardware, therefore with low costs, to actuate a plurality of clutches.
Description
Technical field
The present invention relates to activate the hydraulic actuator device of clutch.Specifically, the present invention relates to hydraulic actuator device for the multi-clutch transmission clutch of actuating automobile.
Background technique
Be used for gear-box (ASG), double clutch or the multi-clutch transmission device (TCT) of auto-changing and the clutch of separable power distribution device transmission device and ransaxle, all be configured to dry type or wet clutch.Their actuating is not that electromechanical is exactly hydraulic type, and wherein, hydraulic actuating provides plurality of advantages because the specific power of actuator is high for the entity arrangements in the transmission.Therefore, clutch can directly be activated (with so-called " central engagement device or take off gearing device "), can avoid the frictional loss that adds owing to the cause of mechanical motion drive mechanism etc.In the transmission or the layout between motor and the transmission device, also provide than the electromechanical actuating system superior hold advantage, the electromechanical actuating system is the outstanding profile that surpasses transmission device often, therefore hinders the installation of transmission device in motor vehicle.
Known hydraulic actuator device is (for example, referring to DE A-4309901, Fig. 1; DE A-19637001, Figure 27; DE A-19950443, Figure 11 F; ) usually formed by the pipeline of pressure generating unit or pumping and storage element (so-called " power cell "), valve group, transmitting fluid and actuator or cylinder body itself, the valve group has several electromagnetic actuating valves, be used for hydraulic energy is assigned to each actuator, alternatively also can with the sensing system of one, be used for determining the position of setting member.Be used for the actuating of hydraulic actuator device of the multi-clutch transmission device of motor vehicle, usually implement by means of motion control unit or senior vehicle computer.
Shortcoming with this kind hydraulic actuator device of storage element is, the pressure medium that is used for the filling storage element, namely, hydraulic fluid, must be pumped to the stress level far above required pressure maximum in the actuator, so that after bleeding off the fluid of requested number, still can provide the operation pressure of requirement, this is disadvantageous for energy, has reduced widely the efficient of device.In addition, solenoid valve mainly is configured to guiding valve, owing to this valve closely allowable clearance need the fluid of high level totally to spend, and often require the filtration measure.Yet used guiding valve has the leakage of a great deal of, and this can cause the complete emptying of storage element through the corresponding operation period, and its result first activates late in filling storage element time delay.Also have,, for example travel on expressway not in the situation of travelling of shift at gear, therefore need regular compartment of terrain again to the storage element pressurising, this is disadvantageous equally for energy.At last, in transmission device, occupy the installing space of a great deal of with the valve group of solenoid valve, in described actuator, present maximum price factor.
Summary of the invention
The purpose of this invention is to provide for the actuating automobile especially hydraulic actuator device of multi-clutch transmission clutch, this actuator has been avoided above-mentioned shortcoming, compares with the prior art of general introduction, and it at first has the total efficiency that cost is lower and significantly improve.
This purpose is realized by feature claimed in claim 1.Advantage of the present invention or favourable exploitation is the theme of claim 2 to 4.
According to the present invention, comprise the multiloop pump with motor-drive pump driver for the actuating automobile especially hydraulic actuator device of multi-clutch transmission clutch, at least two pressure circuits with the pump hydraulic connecting, and the container that is used for hydraulic fluid, hydraulic fluid can be transferred to pressure circuit from container by pump, wherein, from pump, each pressure circuit has along the safety check of pump direction obstruction and Electromagnetically actuated ratio choke valve, by means of this valve, corresponding pressure circuit can hydraulically discharge in the mode of stipulating towards the direction of container, and be positioned at the slave cylinder that output or power provide side and is operably connected to relevant clutch, wherein, pump driver and ratio choke valve electrically are connected to control unit, and this control unit is coordinated the electric actuation of pump driver and ratio choke valve.
If activate one of them clutch, then can carry out the coordination of following concise and to the point elaboration for this clutch: by means of control unit, the ratio choke valve in corresponding pressure loop is activated by electromagnetic ground, and the driving of startup pump, the pressure that forms in this pressure circuit thus hydraulically acts on the corresponding slave cylinder, and slave cylinder activates again clutch.When required pressure reaches in the corresponding pressure loop, just can stop pump and drive, in this case, the pressure between the safety check of this pressure circuit and the ratio choke valve remains locked in the position and continues to act on the corresponding slave cylinder.Require consistently with corresponding actuating, then this ratio choke valve can be activated by control unit, so that relevant pressure loop (with therefore corresponding slave cylinder) hydraulically discharges in prescribed way towards the direction of container.In given situation, by other pressure circuit, even side by side can activate in a similar manner other clutch.
Therefore, with expense quite low on conceptive simple mode and the technology hardware (therefore low-cost), with regard to a plurality of clutches in the actuatable motor vehicle especially multi-clutch transmission, and need not for this purpose storage element, or need guiding valve (with the therefore oily degree of purity of high level).Because only will activated at some clutches, and only be actuated into and produce motion at corresponding slave cylinder place and when needing the degree of the necessary pressure of operation in the corresponding pressure loop, just only have a pump driver must be provided electric current, so pressure balance is better than aforesaid prior art.
In principle, in the coordination of the current delivery of pump driver and ratio choke valve, only have with computation model and just might be operated by control unit, this computation model has especially been considered the known dependence relation between following two aspects, on the one hand, the volume flowrate of the current delivery of pump driver, the rotating speed of pump and generation, on the other hand, the useful area of hydraulic pressure and the power that is applied on the respective clutch in the pressure circuit.Yet, be preferably, if each pressure circuit has pressure transducer, the detectable pressure that actually exists in corresponding slave cylinder place then, and being fed to control unit, control unit activates corresponding ratio choke valve thus suitably, and the pump in given situation drives.
Preferably, be in each ratio choke valve in the non-actuated condition and switch to direct current zero and arrange, just can make in the relevant pressure loop and do not have pressure initiation thereby valve is not applied electric current.Because in each situation, two elements (pump driver and ratio choke valve) therefore must activated, in order to start motion at corresponding servo valve place, improved significantly the reliability for false activations.
At last, be preferably, if the first clutch cooling unit is connected between the outlet of ratio choke valve and container of the first pressure circuit, and link to each other with the clutch of the slave cylinder that is operably connected to the second pressure circuit, and the second clutch cooling unit is connected between the outlet of ratio choke valve and container of the second pressure circuit, and link to each other with the clutch of the slave cylinder that is operably connected to the first pressure circuit, the hydraulic fluid that then flows out from the first pressure circuit, just can be used to cool off the clutch at the second pressure circuit place by means of the first clutch cooling unit, and from the hydraulic fluid that the second pressure circuit flows out, just can be used to cool off the clutch at the first pressure circuit place by means of the second clutch cooling unit.Therefore, the clutch that has just activated can be advantageously by the cooling of the hydraulic fluid in outflow pressure loop, this loop links to each other with the clutch that does not activated at present, basically not by means of its ratio choke valve pressure.
This cooling principle obviously can be displaced to the system with two above clutches without any problems.In the situation of three clutches, for example, actuator can comprise for the first pressure circuit that activates first clutch, be used for activating the second pressure circuit of second clutch, be used for activating the 3rd pressure circuit of three-clutch, wherein, the first pressure circuit has the first ratio choke valve, the first clutch cooling unit is connected to the outlet of this choke valve, the second pressure circuit has the second ratio choke valve, the second clutch cooling unit is connected to the outlet of this choke valve, the 3rd pressure circuit has the 3rd ratio choke valve, the three-clutch cooling unit is connected to the outlet of this choke valve, wherein, the first clutch cooling unit can link to each other with second clutch, and the second clutch cooling unit can link to each other with three-clutch, at last, the three-clutch cooling unit links to each other with first clutch.This program can be similar with three above clutches.
Description of drawings
Below with reference to schematic figures, at length explain the present invention according to preferred embodiment, in the accompanying drawing, identical reference character characterizes same or similar parts, in some given situation, reference character is accompanied by single apostrophe (') or two apostrophe ("), in the accompanying drawing:
Fig. 1 shows the circuit diagram for the hydraulic actuator device that activates two clutches, for example, such as the double clutch transmissions according to the motor vehicle of first embodiment of the invention, wherein, also provide to be used for two clutch coolings that are configured to wet clutch, and
Fig. 2 shows the circuit diagram for the hydraulic actuator device that activates three clutches, these die clutch construction become dry clutch, as according to second embodiment of the invention, hydraulic actuator device for example is used for the hybrid drive train of hybrid vehicle, wherein, three driver parts (petrol engine, asynchronous motor and flywheel) are by means of jack shaft, by activating suitably three dry clutches and stepless transmission, can provide power to the wheel of hybrid vehicle.
Because the professional person understands element and its function that these are operably connected by means of clutch fully, therefore in order to understand the present invention its explanation is seemed no longer necessary, for by means of clutch (namely, the explanation of the element that the corresponding component of double clutch transmission or hybrid type drivetrain) is operably connected all is omitted in the accompanying drawings with in the following description.
Embodiment
In Fig. 1, the total expressions of reference character 10 activate two wet clutches 12,12 ' hydraulic actuator device.As to be described in detail below, hydraulic actuator device 10 comprises multiloop (being the double loop here) pump 14, this pump has motor-drive pump driver M, in the embodiment shown, two pressure circuits 16 that hydraulically are connected with pump 14,16 ' and be used for the container 18 of hydraulic fluid are arranged, and hydraulic fluid can be transferred to pressure circuit 16,16 ' from container by pump 14.Each pressure circuit 16,16 ' comprises from pump 14 successively: along the safety check 20 of pump 14 directions obstruction, 20 ' and Electromagnetically actuated ratio choke valve 22,22 ', by means of this valve, corresponding pressure circuit 16,16 ' can hydraulically discharge in the mode of stipulating towards the direction of container 18, and be positioned at outlet side and operationally be connected respectively to relevant wet clutch 12,12 ' slave cylinder 24,24 ', wherein, pump driver M and ratio choke valve 22,22 ' electrically is connected to control unit ECU, and this control unit produces and coordinate pump driver M and ratio choke valve 22,22 ' electric actuation.
Pump 14 has pump intake 26, and it hydraulically is connected to container 18 by means of pumping tube 28.In addition, pump 14 also has two pump discharges 30,30 ', and they link to each other with pressure circuit 16,16 ' pressure line 32,32 '.Spendable pump type for example is gear pump, roller cavity pump, vane pump and radially or axial piston pump, wherein, with the parallel connection of displacement component and/or the appropriate designs of pump case, guaranteeing a plurality of loops in known mode itself, for example is in the situation with the double-stroke vane pump of the oval stroke loop type of stator.For this application, if pump 14 is configured to the steady flow pump, its desired speed to pump driver M provides constant volume flowrate, and is then just enough.Pump driver M alternatively adopts rotating speed controlled, in order to can react on possible pressure surge, and also can do " adjusting motion " to hydraulic fluid in the pressure circuit 16,16 ' when slowly running.For this reason, apply electric current or actuated pump driver M by means of 33 pairs of pump drivers of feed cable M, this feed cable 33 is shown in broken lines in Fig. 1, and feed cable 33 electrically is connected with control unit ECU.
Therefore, ratio choke valve 22,22 ' comprises the valve casing 48,48 ' of three chambers, and it has armature chamber 50,50 ', flows out stream chamber 52,52 ' and pressure chamber 54,54 ', and wherein, pressure connector 46,46 ' leads to described pressure chamber 54,54 '.The magnetic drives 56 that is consisted of by ferromagnetism armature and magnet coil, 56 ' at least part of with one heart around armature, and be attached on armature chamber 50,50 ' the radial wall (particular of magnetic drives does not at length illustrate in the drawings), this magnetic drives 56,56 ' is contained in the armature chamber 50,50 '.Protrude into the valve pin 58,58 ' that flows out in the stream chamber 52,52 ' with sealing means and centrally be installed on the armature of piston-like, this valve pin 58,58 ' can axially displacement in armature chamber 50,50 '.When electric current was applied to magnetic drives 56,56 ' when upper, valve pin 58,58 ' by armature along valve casing 48,48 ' in prescribed way displacement of direction.Can form by means of feed cable 59,59 ' magnetic drives 56,56 ' is applied electric current, cable is shown in broken lines in Fig. 1, and cable electrically is connected with control unit ECU.
The pressure chamber 54 that diameter is less, 54 ' is connected with outflow stream chamber 52,52 '.Ring-shaped valve seats 62,62 ' is formed on pressure chamber 54, place, 54 ' end, this end is positioned at flows out the stream chamber side, with respect to valve casing 48,48 ' central axis centering, and going out valve clearance with valve body 60,60 ' boundary, this valve clearance has the direct current cross section corresponding to ratio choke valve 22,22 ' chokes cross section.The recovery spring 64,64 ' that pushing valve body 60,60 ' is resisted against on magnetic drives 56,56 ' the valve pin 58,58 ' is arranged in the pressure chamber 54,54 '.
Arrange in the (not shown) at ratio choke valve 22,22 ' direct current zero, valve body 60,60 ' and valve seat 62,62 ' between corresponding valve clearance by recover spring 64,64 ' restoring force is opened to maximum, wherein, magnetic drives 56,56 ' armature by means of valve body 60,60 ' and valve pin 58,58 ' directly pushing be resisted against away from the boss (not shown) that flows out stream chamber 52,52 ' place, armature chamber 50,50 ' end.The stroke of armature maximum possible in armature chamber 50,50 ', at least corresponding to valve body 60,60 ' and valve seat 62,62 ' between the Turn Off Path of valve clearance, so by means of magnetic drives 56,56 ', valve clearance can arrange in prescribed way by valve pin 58,58 ' axial displacement.
At last, each ratio choke valve 22,22 ' has to lead to and flows out stream chamber 52,52 ' outflow stream connector 66,66 '.By means of flowing out stream connector 66,66 ', hydraulic fluid flow through (in given situation) valve body 60,60 ' and valve seat 62,62 ' between after the valve clearance opened, can essentially no pressure ground outflow ratio choke valve 22,22 '.For this reason, flowing out stream pipeline 68,68 ' is connected with each outflow stream connector 66,66 '.
In addition, as can be seen from Fig. 1, each pressure circuit 16,16 ' has pressure transducer 70,70 '.Pressure transducer 70,70 ' by means of hydrostatic sensor line 72,72 ' be connected between corresponding safety check 20,20 ' and corresponding slave cylinder 24,24 ' between relevant pressure pipeline 32,32 ', therefore, survey corresponding slave cylinder 24,24 ' and locate in esse hydraulic pressure.Electrical signal line 74,74 ' Bonding pressure sensor 70,70 ' and control unit ECU.
In addition, in the embodiment shown in fig. 1, realize wet clutch 12,12 ' clutch cooling.In this, first clutch cooling unit 76 is connected between one of ratio choke valve 22 outlet and container 18 of outflow stream connector 66 of formation the first pressure circuit 16 of ratio choke valve 22, and link to each other with the wet clutch 12 ' of the slave cylinder 24 ' that is operably connected to the second pressure circuit 16 ', and second clutch cooling unit 76 ' is connected between the outflow stream connector 66 ' and container 18 of ratio choke valve 22 ' outlet of formation the second pressure circuit 16 ' of ratio choke valve 22 ', and links to each other with the wet clutch 12 of the slave cylinder 24 that is operably connected to the first pressure circuit 16.As shown in Figure 1, apparatus for cooling clutch 76,76 ' for example can comprise container 78,78 ', they are by means of flowing out stream pipeline 68,68 ' supply with hydraulic fluid, and by one or more chokes points 80,80 ' supplying hydraulic fluid drop by drop from each container, to cool off corresponding wet clutch 12,12 ', finally again with fluid collection in container 18.Its result, hydraulic fluid from 16 outflows of the first pressure circuit, just can be used to cool off the wet clutch 12 ' that the second pressure circuit 16 ' is located by first clutch cooling unit 76, and from the hydraulic fluid that the second pressure circuit 16 ' flows out, just can be used to cool off the wet clutch 12 at the first pressure circuit 16 places by means of second clutch cooling unit 76 '.
In system shown in Figure 1, with two wet clutches 12,12 ' and slave cylinder 24,24 ' structure as gearing device, for example, following program just can be used for above-mentioned hydraulic actuator device 10, wherein, control unit ECU activates and coordinates pump driver M and ratio choke valve 22,22 ' suitably.
When this system did not activated, two wet clutches 12,12 ' were separated.In the situation that need to cool off wet clutch 12,12 ', hydraulic actuator device 10 transmits electric current in the situation of complete no current or pump driver M, so that pump 14 is transferred to hydraulic fluid in the pressure circuit 16,16 ' from container 18, and ratio choke valve 22,22 ' keeps no current, therefore is arranged on during its direct current zero arranges.Its result, by means of by flowing out stream pipeline 68,68 ' from ratio choke valve 22, the 22 ' volume flow that flows out (volume flow from valve 22 to clutch 12 ' and 12 the volume flow from valve 22 ' to clutch), wet clutch 12,12 ' is by apparatus for cooling clutch 76,76 ' generation cooling each other.
For example, engagement for the wet clutch 12 on Fig. 1 right side, pump driver M and corresponding ratio choke valve 22(are, on the right side) conduction current, so that pump 14 is at pressure circuit 16 and ratio choke valve 22 interior transmission hydraulic fluids, magnetic drives 56 is tried hard to recommend pressure valve body 60 towards valve seat 62 by what valve pin 58 opposings recovered springs 64.Therefore, in the pressure chamber 54 of ratio choke valve 22 and therefore mineralization pressure between safety check 20 and slave cylinder 24, this pressure acts on its piston 36 by means of the pressure chamber 38 of slave cylinder 24, finally causes piston rod 42 displacements and meshes wet clutch 12.Simultaneously in another pressure circuit 16 ' by the hydraulic fluid of pump 14 pumpings, passing ratio choke valve 22 ' flows out, therefore ratio choke valve 22 ' non-conducting electric current leads to second clutch cooling unit 76 ' by means of flowing out stream pipeline 68 ', therefore is used for the wet clutch 12 of cooled engagement.In a similar fashion, the wet clutch 12 ' on Fig. 1 left side can be engaged, or two wet clutches 12,12 ' also can mesh simultaneously, and wherein, in a rear situation, if container 78,78 ' is empty, then cooling occurs.
If system mode will maintain the wet clutch 12,12 ' of at least one engagement, for example, wet clutch 12 among Fig. 1 on the right side, so, corresponding ratio choke valve 22(namely, the valve among Fig. 1 on the right side) come conduction current according to the desired point of load, so, by means of ratio choke valve 22 and the safety check 20 of biasing, keep the pressure at slave cylinder 24 places, move in this case and need not pump 14.In a similar fashion, among Fig. 1 on the left side, wet clutch 12 ' can remain in the state of engagement, or also can two wet clutch 12,12 ' keep simultaneously engagement.
In addition, as following the summary, the transmission to another of torque from wet clutch 12,12 ' can occur, for example, from following system mode: clutch 12 engagements of right-hand side, the clutch 12 ' of left-hand side breaks away from engagement, valve 22 conduction current of right-hand side, valve 22 ' and the pump driver M non-conducting electric current of left-hand side.The initial electric current that passes into pump driver M that utilizes of control unit ECU starts by pump 14.Then, the ratio choke valve 22 that is used for the wet clutch 12 on Fig. 1 right side is released continuously, wherein, the valve electric current that magnetic drives 56 places exist, regulate according to known clutch characteristics curve, this curve is stored in the control unit ECU of right-hand side wet clutch 12, so that the pressure in the pressure circuit 16 descends suitably, therefore the piston 36 in the slave cylinder 24 moves to left according to the implication of defined " breaking away from engagement ".Simultaneously, the ratio choke valve 22 ' conduction current that is used for the wet clutch 12 ' on Fig. 1 left side, wherein, the valve electric current that magnetic drives 56 ' is located to exist, regulate according to same known clutch characteristics curve, this curve is stored in the control unit ECU of left-hand side wet clutch 12 ', so that the pressure in the pressure circuit 16 ' rises suitably, the piston 36 ' in the slave cylinder 24 ' therefore moves to right according to the implication of defined " engagement ".For example, in the situation of double clutch transmission, ratio choke valve 22,22 ' is located electric current and is regulated and will match each other, and need not to interrupt tractive force switching.In case reach predetermined pressure in the pressure circuit 16,16 ', and the piston rod 42,42 ' that slave cylinder 24,24 ' is located meets the requirements of the position, control unit ECU is just by interrupting that the electric current that applies of pump driver M is closed pump 14.Obviously, the transmission of torque from Fig. 1 " left side " to Fig. 1 " right side " can occur in a similar manner.
By control unit ECU, pump driver M and ratio choke valve 22,22 ' switched to does not have electric current fully, and all systems just can unload.
Obviously, according to corresponding drive mechanism, by further arrangement branch, above-mentioned hydraulic actuator device also can be exaggerated, each branch comprises other pump stage, other safety check and other ratio choke valve, their activate requirement and can side by side operate according to corresponding, or also can be in time deviation each other.
The below describes the second embodiment with reference to Fig. 2, only the part that is different from reference to described the first embodiment of Fig. 1 is described.
Compare the first embodiment, hydraulic actuator device 10 ' according to Fig. 2 comprises three loop pump 14 ', for example, it can be with the triple-travel vane pump of special salient stator wheel track (with rounding " triangle "), and allowing each to turn has several suction and pressure strokes.Three pressures loop 16,16 ', 16 altogether " be connected to pump 14 ', they are not different from the first embodiment's pressure circuit 16,16 '.Yet, the second embodiment's slave cylinder 24,24 ', 24 " and the clutch (for clear for the purpose of, not shown among Fig. 2) that activates is three dry clutches, they do not need fluid cooling and thus the first embodiment's apparatus for cooling clutch to a certain extent.Therefore, compare with the first embodiment, in a second embodiment, flow out stream pipeline 68,68 ', 68 " directly from ratio choke valve 22,22 ', 22 " turn back to container 18.
The professional person obviously can understand, in this embodiment's situation, slave cylinder 24,24 ', 24 " activate requirement according to corresponding; can hydraulically load or release, by control unit ECU suitably actuated pump driver M and ratio choke valve 22,22 ', 22 ", in order to produce corresponding engagement or out-of-gear motion, wherein, especially, on energy and technology hardware, aspect the relative little expense, keep corresponding system mode to occur highly beneficially.
The present invention discloses for the actuating automobile especially hydraulic actuator device of multi-clutch transmission clutch, it comprises: the multiloop pump with motor-drive pump driver, at least two pressure circuits that hydraulically are connected with pump, and the container that is used for hydraulic fluid, hydraulic fluid can be transferred to pressure circuit from container by pump.In this, from pump begins, each pressure circuit has: along the safety check of pump direction obstruction, Electromagnetically actuated ratio choke valve, by means of this valve, corresponding pressure circuit can hydraulically discharge towards the direction of the container mode with regulation, and is positioned at outlet side and is operably connected to the slave cylinder of relevant clutch.Pump driver and ratio choke valve electrically are connected to control unit, and this control unit is coordinated the electric actuation of pump driver and ratio choke valve.Its result just can accomplish the clutch actuation of high total efficiency with low cost.
List of numerals
10,10 ' hydraulic actuator device
12,12 ' wet clutch
14 double-loop pumps
14 ' three loop pump
16,16 ', 16 " pressure circuit
18 containers
20,20 ', 20 " safety check
22,22 ', 22 " ratio choke valve
24,24 ', 24 " slave cylinder
26 pump intakes
28 aspiration line
30,30 ', 30 " pump discharge
32,32 ', 32 " pressure line
33 feed cables
34,34 ' cylinder shell
36,36 ' piston
38,38 ' pressure chamber
40,40 ' pressure connector
42,42 ' piston rod
44,44 ', 44 " valve pipeline
46,46 ' pressure connector
48,48 ' valve casing
50,50 ' armature chamber
52,52 ' flows out the stream chamber
54,54 ' pressure chamber
56,56 ' magnetic drives
58,58 ' valve pin
59,59 ', 59 " feed cable
60,60 ' valve body
62,62 ' valve seat
64,64 ' recovers spring
66,66 ' flows out stream connector
68,68 ', 68 " flow out the stream pipeline
70,70 ', 70 " pressure transducer
72,72 ', 72 " pickup wire
74,74 ', 74 " signaling line
76 first clutch cooling units
76 ' second clutch cooling unit
78,78 ' container
80,80 ' chokes points
The ECU control unit
M pump driver
Claims (4)
1. comprising for the actuating automobile especially hydraulic actuator device (10,10 ') of multi-clutch transmission clutch (12,12 '):
Multiloop pump (14,14 ') with motor-drive pump driver (M),
With at least two pressure circuits of pump (14,14 ') hydraulic connecting (16,16 ', 16 "), and
The container (18) that is used for hydraulic fluid, the flow of pressurized physical efficiency is transferred to pressure circuit (16,16 ', 16 ") by pump (14,14 ') from container,
Wherein, from pump (14,14 '), each pressure circuit (16,16 ', 16 ") comprising:
The safety check that blocks along pump (14,14 ') direction (20,20 ', 20 "),
Electromagnetically actuated ratio choke valve (22,22 ', 22 "), by means of this valve, corresponding pressure circuit (16,16 ', 16 ") can discharge with the mode hydraulic pressure of stipulating towards the direction of container (18), and
Be positioned at outlet side and may be operably coupled to the relevant clutch slave cylinder of (12,12 ') (24,24 ', 24 "), and
Wherein, pump driver (M) and ratio choke valve (22,22 ', 22 ") are connected electrically to control unit (ECU), and this control unit is coordinated the electric actuation of pump driver (M) and ratio choke valve (22,22 ', 22 ").
2. actuator as claimed in claim 1 (10,10 ') is characterized in that, each pressure circuit (16,16 ', 16 ") comprises pressure transducer (70,70 ', 70 ").
3. actuator as claimed in claim 1 or 2 (10,10 ') is characterized in that, will be in ratio choke valve in the non-actuated condition (22,22 ', 22 ") and switch to direct current zero and arrange.
4. such as each described actuator (10) in the above-mentioned claim, it is characterized in that, if first clutch cooling unit (76) is connected between the outlet (66) and container (18) of ratio choke valve (22) of the first pressure circuit (16), and link to each other with the clutch (12 ') of the slave cylinder (24 ') that is operably connected to the second pressure circuit (16 '), and second clutch cooling unit (76 ') is connected between ratio choke valve (22 ') outlet (66 ') and the container (18) of the second pressure circuit (16 '), and link to each other with the clutch (12) of the slave cylinder that is operably connected to the first pressure circuit (16) (24), the hydraulic fluid that then flows out from the first pressure circuit (16), just can be used for cooling off the clutch (12 ') that the second pressure circuit (16 ') is located by means of first clutch cooling unit (76), and from the hydraulic fluid that the second pressure circuit (16 ') flows out, just can be used for cooling off the clutch (12) that the first pressure circuit (16) is located by means of second clutch cooling unit (76 ').
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102011105648.7 | 2011-06-07 | ||
| DE102011105648A DE102011105648A1 (en) | 2011-06-07 | 2011-06-07 | Hydraulic actuator for the actuation of clutches in particular a multi-clutch transmission for motor vehicles |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102996789A true CN102996789A (en) | 2013-03-27 |
| CN102996789B CN102996789B (en) | 2015-10-28 |
Family
ID=46229172
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201210185047.0A Active CN102996789B (en) | 2011-06-07 | 2012-06-06 | For the hydraulic actuator device of clutch in actuating automobile especially multi-clutch transmission |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US8939268B2 (en) |
| EP (1) | EP2532914B1 (en) |
| JP (1) | JP5705789B2 (en) |
| CN (1) | CN102996789B (en) |
| DE (1) | DE102011105648A1 (en) |
| HK (1) | HK1177630A1 (en) |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN103470751A (en) * | 2013-09-29 | 2013-12-25 | 长城汽车股份有限公司 | Hybrid electric vehicle and double clutch automatic transmission used for hybrid electric vehicle |
| CN104863991A (en) * | 2014-02-21 | 2015-08-26 | 格特拉格传动机构和齿轮工厂赫尔曼·哈根迈尔有限公司&两合公司 | Coupling assembly, motor vehicle power train and coupling control method |
| CN106246899A (en) * | 2015-06-11 | 2016-12-21 | 腓特烈斯港齿轮工厂股份公司 | For controlling the method that the torque of the switching device of force closure is transmitted |
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| CN103470751A (en) * | 2013-09-29 | 2013-12-25 | 长城汽车股份有限公司 | Hybrid electric vehicle and double clutch automatic transmission used for hybrid electric vehicle |
| CN104863991A (en) * | 2014-02-21 | 2015-08-26 | 格特拉格传动机构和齿轮工厂赫尔曼·哈根迈尔有限公司&两合公司 | Coupling assembly, motor vehicle power train and coupling control method |
| CN106795965B (en) * | 2014-07-31 | 2019-07-23 | Fte汽车股份有限公司 | For activating the device for hydraulically actuating of multiple setting elements in motor vehicle transmission |
| CN106795965A (en) * | 2014-07-31 | 2017-05-31 | Fte汽车股份有限公司 | Device for hydraulically actuating for activating the actuator in motor vehicle transmission |
| CN106246899A (en) * | 2015-06-11 | 2016-12-21 | 腓特烈斯港齿轮工厂股份公司 | For controlling the method that the torque of the switching device of force closure is transmitted |
| CN106246899B (en) * | 2015-06-11 | 2019-11-22 | 腓特烈斯港齿轮工厂股份公司 | Method for controlling the torque transfer of the switching element of force closure |
| CN106594111A (en) * | 2015-10-14 | 2017-04-26 | 重庆齿轮箱有限责任公司 | Multi-clutch oil way control system and gear box |
| CN108291590B (en) * | 2015-12-18 | 2020-04-07 | 舍弗勒技术股份两合公司 | Pump actuator for clutch and gear shift actuation in a transmission of a motor vehicle |
| CN108291590A (en) * | 2015-12-18 | 2018-07-17 | 舍弗勒技术股份两合公司 | Pump actuator for carrying out clutch and selector actuating in the speed changer of motor vehicle |
| CN106917868A (en) * | 2015-12-25 | 2017-07-04 | 北理慧动（常熟）车辆科技有限公司 | For the electricity powered clutch actuating mechanism of Hydromechanical transmission |
| CN110709605A (en) * | 2017-06-09 | 2020-01-17 | 株式会社电装 | Electric pump device |
| CN107965572A (en) * | 2017-11-06 | 2018-04-27 | 北京理工大学 | A kind of automatic transmission electrohydraulic control system |
| CN107965572B (en) * | 2017-11-06 | 2020-06-26 | 北京理工大学 | Electro-hydraulic control system for automatic transmission |
| CN110894874A (en) * | 2018-09-12 | 2020-03-20 | Fte汽车有限责任公司 | Pump unit for providing hydraulic pressure for actuating an actuator in a motor vehicle drive train |
| CN110939722A (en) * | 2018-09-21 | 2020-03-31 | Fte汽车有限责任公司 | Hydraulic device for cooling at least two wet clutches in a motor vehicle |
| CN111089126A (en) * | 2018-10-24 | 2020-05-01 | Fte汽车有限责任公司 | Hydraulic clutch actuator |
| CN111089162A (en) * | 2018-10-24 | 2020-05-01 | Fte汽车有限责任公司 | Hydraulic transmission actuator, assembly with same and transmission for power train |
| CN111089163A (en) * | 2018-10-24 | 2020-05-01 | Fte汽车有限责任公司 | Hydraulic gearbox actuator |
| CN111089126B (en) * | 2018-10-24 | 2023-01-17 | Fte汽车有限责任公司 | Hydraulic clutch actuator |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2013057396A (en) | 2013-03-28 |
| EP2532914A1 (en) | 2012-12-12 |
| HK1177630A1 (en) | 2013-08-23 |
| CN102996789B (en) | 2015-10-28 |
| JP5705789B2 (en) | 2015-04-22 |
| EP2532914B1 (en) | 2020-07-29 |
| US20120312655A1 (en) | 2012-12-13 |
| US8939268B2 (en) | 2015-01-27 |
| DE102011105648A1 (en) | 2012-12-13 |
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